Pump



W. A. KATES May 19, 1942.

PUMP

Filed Dec. 21; 1959 4 Sheets-Sheet 1 May. 19, 1942. w KATES 2,283,263

PUMP 1 Filed Dec. 21, 1959 4 Sheets-Sheet 2 W. A. KATES May 19, 1942.

PUMP

' F iled .Dec. 21, 1939 4 Sheets-Sheet 3 May 19, 1942. w. A. KATES PUMP Filed Dec. 21, 1939 4Sheets-Sheet 4 Patented May 19, 1942 PUMP Willard A. Kates, Corning, N. Y., asslgnor to Corning Glass Works, Corning, N. Y., a corporation of New York Application December 21, 1939, Serial N0. 310,432

7 Claims.

This invention relates to pumps, and more par-,

ticularly to a pump assemblage of casing, impeller, driving means, and frame for the casing. wherein the casing and impeller parts are formed of corrosion resisting material and, therefore, particularly applicable to the handling of acids, and

the like.

An object of the invention is to provide a pump construction, wherein substantially all of the parts that will contact in any manner with the fluid being pumped are formed of corrosion resisting material.

Another object of the invention concerns a centrifugal liquid pump in which the pump elements that come in contact with the fluids being pumped are formed of vitreous material, such as glass, or like refractory material. In this connection it has been found that glass is the most desirable because of its high resistance to corrosion from most acids, and because of its adaptability in handling liquids containing'acids under the most efficient sanitary conditions.

Another object of the invention particularly concerns all glass pumps and means whereby they may be satisfactorily sealed against escape of fluid without, in so doing, developing sufllcient localized heat to destroy the parts by differential expansion.

However, in the use of such materials for pump elements, the frangible nature of the materials under various conditions of stress and temperature is a hazard, and accordingly it is a further object to construct a pump in which is provided a strong metal frame, or housing, which not only functions in the operation of the pump, but it is devised to support the pump casing under controlled pressure, in a manner to minimize crushing or breakage, and also to afford protection from flying fragments, in the event that a breakage should occur.

ne feature of the invention is concerned with the mounting of the pump casing within such a frame or housing in a manner which is protective to the casing while, at the same time,

holding the casing firmly and securely during ing box elements and retaining members which promotes ease and dispatch in the assembly and disassembly.

A further feature of the invention is the provision of means within the pump chamber by which the pressure of fluid on the stuffing within the stuflingbox is materially reduced so that an effective seal may be maintained with a limited degree of pressure and a corresponding relatively slight generation of heat within the sealing relatively low tensile strength, and therefore calbond without, however, placing undue stress upon the impeller.

The-latter object contemplates the formation of a joint between one member which acts as a moving driving member, and another member which is driven by said moving member, of more or less general application, but particularly adapted to uses in connection with a pump of the type herein described.

The invention has particular application, but is by no means limited thereby, in joining a rotary glass impeller of a pump, to a metal driving member or shaft of the type illustrated and claimed in a co-pending U. S. application of Harold E. Adams, Serial No. 275,755, flled May 25, 1939.

A particular problem arises in the joining 'of a frangible rotary member, such as an impeller, constructed of glass, to a metal driving member. The strength of the materials in tension, in a rotatable member fromed of such materials as herein contemplated, makes it imperative that the joint between the metal driver and the fran- 'gible driven member be somewhat resilient, yet

and replacement of worn parts, and to this end there is disclosed a novel arrangement of 11:-

free of play. By the construction of the present invention a joint is provided which overcomes these difficulties in a very eflicient and economical manner, and the invention contemplates the use of a bonding material between the driving and driven members, which is resilient in nature and has a lower modulus of elasticity than the A further feature of-the invention is the provision of a joint structure employing a bonding medium between two preformed parts in which any possible shrinkage of the bonding material will result in afurther strengthening of the mechanical interengagement of said parts;

Although the construction and operation of .preferred forms of the invention are illustrated and described, it will be understood that they are intended only as illustrative and not as limiting, it being understood that the invention is not to be limited, other than as defined by the claims hereinafter appended.

To the attainment of the foregoing, and other objects which will appear as the description proceeds, reference is made to the accompanying drawings, in which:

,Fig, 1 is a sectional elevation of a centrifugal pump showing one application of the present invention therewith;

Fig. 2 is an exploded perspective view partly broken away, illustratiing a joint constructed in accordance with the present invention, be-

-tween a metal drive member and an impeller removed from the drive shaft and without the bonding material; I

Fig. 3 is an enlarged fragmentary sectional elevation through the drive and driven member, removed from the drive shaft;

Fig. 4 is a section taken substantially on the plane of line 44 of Fig. 3 which section is taken through the radial grooves;

Fig. 4a is a fragmentary enlargement of a part of Fig. 4;

Fig. 5 is a section taken substantially on the plane of lines 5-5 of Fig. 3 when mounted on the drive shaft, said section being taken on a plane spaced from the radial grooves;

Fig. 6 is an elevation of a pump embodying a slightly modified form of frame or housing;

Fig. 7 is a central section taken on the line Il of Fi 6;

Fig. 8 is a fragmentary end elevation of a pump embodying different modifications of frame or housing, and means of joining the housing sections together;

Fig, 9 is a side elevation of the pump shown in Fig. 8; and

Fig. 10 is a detail partly in section showing the mode of securing the frame sections together in the form of invention illustrated in Figs. 8 and 9.

Referring now more particularly to the drawings, wherein like reference numerals designate like parts, and with particular reference to Figs. 1 to 5, it will be seen that the pump assemblage comprises a supporting frame or housing A, preferably made of metal, having acid resisting qualities, or acid resisting coatings, a sectional centrifugal pump casing indicated generally at B, which casing is formed of a head section! and a crown or volute portion H. In the form of pump casing selected for illustration, the sections 10 and II are made of refractory vitreous material such as glass, for accommodating the pumping of highly corrosive fluids, and the casing sections are secured together in a suitably clamped relation, as hereinafter described.

A centrifugal pump chamber I3 is formed by the this extension provides the stuffing box or seal chamber for the packing or sealing elements ll through which the hub l8 of the impeller I extends. In practice, the'packing and sealing elements I'I provides. mechanical seal between the chamber and the hub to seal the pump chamber from the exterior of the casing and prevent leakage of the liquid being pumped, and at the same time prevent air from entering the casing and impairing the suction of the pump. While the preferred form of the pump of the present invention is made of glass substantially as shown in the drawings, it is obvious that certain of the mechanical details therein illustrated may be modified without eliminating the features of the present invention. Similarly the impeller and casing may be made of high siliconv iron, or high chromium, or high nickel steel, all of which are sufiiciently resistant to corrosion for application to pumping certain corrosive liquids while retaining certain other features of the invention. However, these metals like glass, are very difficult to machine and are usually machined by grinding, which characteristics are the same as glass used in the preferred embodiment in the present disclosure.

In order to produce a successful glass or vitreous pump capable of handling corrosive liquids, it is essential that all parts of the pump coming in contact with such liquids be formed from glass or whatever resistant material is being employed. In a centrifugal pump of the type disclosed this requires that the shank I8 of the impeller I and the sleeve l5 of the casing B be formed from glass as integral parts of their respective bodies. Thus, the only non-vitreous material exposed to the action of the fluid being handled is the in ner portion of the packing l1. While various glasses are particularly resistant to attack by casing sections l0 and H and in the chamber is is indicated at M, and the outlet port (not shown) leads from the periphery of the casing B. In

1 the center of the volute section, an integral stuifingbox extension or neck I 6 is formed and acids and by alkalies, all glasses, even those commonly referred to as heat resistant, have only a rather limited ability to withstand differential heating and the resultant differential expansion stresses within the glass. This inherent weakness of glass has consistently thwarted all attempts to produce a satisfactory seal for an all glass pump inasmuch as the friction of a packing sufficiently tight to establish a fluid tight seal has generated suflicient heat in the adjacent portions of the glass parts to destroy them.

In the present invention the above difiiculties and weaknesses have been overcome by increasing'the area of the packing IT in contact with shank l8 and by providing on the back or ad- 'mum pressure developed by the pump. On the other hand it is desirable that a certain amount of the fluid being pumped penetrates into thepacking to lubricate the same since otherwise some foreign lubricant must be provided which may dilute or contaminate the material being pumped. In the present structure the size and contours of the secondary vanes V are so chosen with respect to the working vanes V' and the length of the packing I! as to prevent any excesa-aaaaee sive pressure on the packing while'permitting suchseepage as is absolutely required.

While it is feasible to couple metal to metai having suitable elastic limits by the commonly practiced methods of keyways and set screws, suchpractice is not adaptable to vitreous, pottery, or ceramic products, and frangible rigid metals. The primary reason is that the strength of the materials in tension will not permit of a satisfactory coupling. Another reason is because molding and casting of articles from vitreous and allied metal material with precision keyways and set screw openings is extremely difficult, if not impossible, and since vitreous and allied metal materials cannot be machined in conventional ways, grinding must be resorted to, and it isvery expensive to grind keyways and openings for set screws. feasible to dothis, the torsional stresses and strains in set screw and keyway couplings would be localized to the spot of the set screw, or the line of the keyway, which it is desirable to avoid.

Thus, a further problem which arises from the use of glass, pottery, and similar vitreous materials which are relatively weak in tension is that of suitably connecting the frangible impeller I to 'a metal drive shaft C, driven by a prime mover, such as the electric motor M. It will be seen that the joint of the present invention must not only provide a supporting connection between the drive and driven members, but it must also be the instrumentality by'which rotary motion is transmitted to the driven mem ber, whereby the driven member performs work.

. In order to connect the driven member, such as the impeller I, to the driving member, it is desirable to provide the impeller with some character of opening or cavity in which the driving member may be seated, or through which the driving member may extend. Since it is undesirable to permit any part of the prime mover connections to pass through the impeller where they would come in contact with the fluid being pumped, it is preferred to adopt the cavity principle, and in the preferred form of .the invention a longitudinally fluted socket 20 is molded in the impeller hub l8 (Fig. 2). The flutes provide the crests 2| and the intervening valleys or troughs 22. The crests 2| serve as key-like protuber- 'ances, and the valleys 22 serve in the nature of keyways so as to conform to the corresponding configurations on the driving member. The side walls 2| of the crests 2| are preferably parallel to each otherand to the radius passing through the center of the crest, as .shown in Figs. 4, 4a, and 5 for purposes to be hereinafter explained. Across the crests of each of the flutes are axially spaced circumferentially extending grooves 23, connected across the valleys 22 by shallow grooves 24. The grooves 23 form a series of Even though it were ingly functions as a torque distributing memtension, indicated generally at 26, terminating in a flattened transverse tang 21. A radially disposed cavity 23 in the inner wall of the socket 20 receives the tang when it is brought into registration, and cooperates therewith to form a mechanical driving connection between the quill and socket. There will be sufllcient clearance between the tang and cavity to accommodate a layer of cementing or bonding material. The head and reduced part are separated by a radial shoulder 29 that has a semi-circular radially extending groove 30 in its face. The groove 30 forms a vent or riser for excess cementing or bonding material when the quill is inserted in the socket 20, thus allowing the shoulder 29 to be brought up against the free edge of the hub l8 and giving better positioning of the quill in assembling with the impeller, and also providing an index that the cavity between the quill and the hub socket 20 has been completely filled with bonding material during the assembly operation. There is a slight overall taper from the outer to the inner end of the socket 20 in the hub spaced rings substantially interrupted by the valleys 22 in the'wall of the socket 28.

While the hub l8 may be secured directly to the drive shaft ,0, in the manner explained in the present invention, it, has been found to be more practical to interpose an intermediate connection, and toward this end, there is used as the driving member D, a hollow spindle or thimble generally known as a quill, which is made preferably of acid resisting metal.

The quill performs the function of distribut- -rupted by the intervening valleys 32,

and the reduced part 26 of the quill is correspondingly tapered.

The reduced part 26 is formed with flutes slightly smaller than the flutes in the socket so that the crests 3| and the valleys or troughs 32 on the reduced part 26 will leave a clearance with the corresponding crests 2| and valleys 22 in the socket 20 so as to permit a certain amount of thebonding material 3311 to congeal between the confronting surfaces and resiliently lock the hub, and driving or torque distributing member D together. The side walls 3| of the crests 3| are likewise parallehto each other and to the radius passing through the center of the crest. It will be seen that when the quill is assembled in the hub, the crests of the flutes on thehub overlap or overhang the flutes on the quill in a radialv direction, and vice versa, with the bond 33a in between, and this prevents rotary play between the parts.

At the outer end, each of the valleys 32termi- -nates in an outwardly flared pocket 33.

The pocket 33 allows clearance for the ends of the crests 2| of the flutes in the socket should any fins be adhering to them due to faulty casting, molding, or grinding. registers with one of the .pockets 33. Extending across the crests 3| are a plurality of circumferentially extending axially spaced grooves '34,

and these grooves cooperate with the grooves 23 in the crests 2| of the flutes in the hub socket 20 when the quill is assembled in the hub. Like the grooves 23 in the socket 20 of the hub, the grooves 33 form a series of spaced rings inter- These grooves 23 and 34 prevent longitudinal movement between the quill and impeller, while the radially overhanging flutes on the quill and hub prevent rotary movement, when the bonding material 33a is applied.

Along the axis of the quill is a socket 35 which receives the stub drive shaft C, of the prime 4 36 (Figs. 4 and 5) which receives one-half of the key 31, while the other half of the key seats in the keyway 33 on the drive shaft. The quill is selectively positioned on the drive shaft C and locked thereto by the positioning set screw 33 mover M. In the wall of thissocket is a keyway The riser groove 30.

threaded in an opening 40 in. the head 25 of the quill, and a second set screw 42 threaded in an opening 3 in the head 25. The positioning set screw 39 engages with an opening 44 in the stub drive shaft C, and when seated in this opening theimpeller will be locked in its proper position on the shaft. The inner end of the set screw 42 abuts the periphery of the drive shaft C and takes up all play in the parts whereby. any tendency of the impeller to wobble is eliminated.

The quill is anchored to the impeller I by a bonding material 33a. Preferably there is used I an alloy, cement, or bonding material having the characteristic of becoming liquid or thermoplastic und'er heat of a temperature that will not injure the glass when the bonding material 'is applied, although hydraulic cements may also be used. Among the desirable bonding materials are those low melting point alloys generally designated as type metals which have the desirable property of expanding slightly while cooling from a liquid to a solid phase. This property is valuable in the present invention because the irregularity in the surfaces have been specially designed to accommodate such an expanding material.

The preferred way of joining the metal quill to the hub I8 is to heat the quill and impeller to a temperature approximately that of the melting point of the particular composition used. A quantity of the composition slightly in excess of that required is placed in the socket. and the hot quill is inserted until shoulder 29 comes up hard against the end of the hub l8. The excess material will meanwhile escape through the vent, or riser 30.- When the' quill is in its inserted position, the crests 2| of the flutes on the socket will substantially register withthe corresponding recesses or valleys 32 in the flutes of the quill. In a like manner, the valleys 22 in the socket '20 receive the crests 3| of the flutes on the reduced part 26. In this position, the extremity of the crests on the flutes on the quill or driving member D, radially overhang, or overlap the extremity of the crests of the flutes in the socket 20 of the impeller or driven member I.

As heretofore pointed out, there will be continuous spaces between the corresponding crests and valleys in the socket 20 of the impeller and reduced part 26 of the metal quill in the assembled relation, and the shoulder 29 will be bearing against the free edge .of the hub IS. The alloy bonding composition will then fill the space between the corresponding crests and valleys of socket 20 and reduced part 26; and also fill the grooves 34 in the crests 3| of the flutes of the quill, and the grooves 23 in the crests 2| of the flutes in the socket.

While the tendency of the preferred-alloys is to expand slightly on congealing, all such alloys and cements will shrink upon further coollog and, if the rate of shrinkage be different from the adjacent glass and metal parts, there will be a slight loosening of the joint. Such loosening is overcome in the preferred form of the invention by the special design of the side walls of the crests 2| and 3|, as previously described. The shrinkage of the bond Me which loosens the joint is primarily in a generally radial direction. Due to the above described configuration of the crests, it will be seen (Fig. 40.) that any contraction' of the bond 33a radially with respect to the quill 26 and hub |l will result in an increased clamping action of the solidified bond against the walls 2| and 3| of the various crests. In this manner a tight joint is ensured regardless of the rate of contraction of the bond.

It is pointed out there is an axial and circumferential bond 33a of bonding material throughout the entire confronting area between the socket in the hub and the reduced part of the quill.

It will be understood that the bond is not an adhesive bond between the metal of the quill 26 and the glass of the hub l8. .The composition will be adhesive or "wet only to the metal of the quill, and not to the glass. Because of the different rate of expansion and contraction between metal and glass, it is not practical to have a bond which is adhesive to both materials. However, the composition when set forms a slightly yieldable cushion sufliciently conformed to produce a good mechanical bond, but yieldable sufliciently to distribute torque. In other words, the composition forms a load distributing coupling effective to maintain shear stress in the glass well below its rupture value.

As a matter of fact, it is not essential to attain adhesion or wetting with respect to the quill, although this is preferable because of contraction in the quill upon cooling thereof. If a bonding material which is not adhesive to the quill is used, then it is desirable to use a material having a coemcient of expansion greater numerically than the coefiicient of ex pansion of the material of the quill, so that the bonding material will shrink tight about the quill on cooling.

As a further variation, if a material is used which provides good adhesion to the quill, then it is not even necessary to form grooves in the quill.

In addition to this bond, .there is the mechanical lock against rotation between the parts, caused by the radial overhang between the flutes. This mechanical lock is augmented by the expansion of the cement into the flutes, and the insertion of the tang 21 into the socketor =keyway 28. From the foregoing it will be obvious that the driving stresses, when the parts are rotating are well distributed throughout the quill.

Then there is the still further mechanical lock against axial, or longitudinal movement between the parts occasioned by the circumferential grooves 23 and 24. These three factors distribute the torsional stresses and strains over a greater area of the drive and driven members than is known to have been applied to any rotary joint.

The following compositions are given by way of example of suitable alloys for.use as bonding materials:

Paces; Percent Bismuth 48. Lead 28. 50 86. 50 Tin 14. 50 O. 50 Antimony 9. 00 13.00

Another and important problem.involved in the construction of pumps, utilizing glass or other ceramic or vitreous materials is found in the assemblage, mounting and adequate support for the pump casing within which is formed the pumping chamber, It is, of course, essential that the pump casing be held firmly and securely,

while at the same time avoiding any tendency to' produce localized strain therein. and also to afford protection from flying fragments, in the event that breakage should occur.

To this end there is provided a sectional metal housing or frame which furnishes a protective guard, as well as adequate support, this sectional housing being suitably clamped under predetermined uniform pressure. I

In Fig. l, the sectional metal housing or frame A provides a support for clamping the sections of the pump casing B together, and also provides the protective guard for the casing. All of the outer metal parts of the present structure, including the housing A may be made of cast iron, or other metal, not necessarily highly resistant to acid or acid vapors, and such metal parts may be plated with acid resisting material, such as cadmium, or covered with rubber base paints, or other suitable acid resistant coating.

, This housing A is preferably formed in two major portions or sections, the inner of which consists of a frame section 50 which maybe suitably braced or bolted if desired, to the .motor M. One convenient and conventional mode of supporting the frame 50 would be by a spider or struts between the housing A and the motor, as illustrated for example in Fig. 9, but any convenient method may be used. The outer section of the housing A comprises an annular flanged member having a flange 52 directed radially inward to embrace a face of the casing section I0, a projecting flange 53 disposed substantially at right angles to the flange 52 to encompass the periphery of the glass section III, and anoutwardly directed flange portion 54 which provides means for securing the section 5| to the-section 50. The section or portion '50 is generally bell shaped to accommodate and encompass th glass casing section II and terminates in its outer peripheral edge with a thickened flange-like section 55, rabbeted, as indicated at 56, to receive the flange 53 of section 5|, and thereby pfovide a mating relation between the two housing or main sections 50 and 5|. The flange 54 is suitably drilled to receive threaded bolts 51 which may be threaded into the flange 55 of section 50.

It will be evident then that the pump casing section I I may be mounted within the bell-shaped housing or frame section 50, the impeller being suitably assembled thereon, and then the pump casing may be completed by placement of the section casing Ill and securing thereof in place by the housing'or frame section 5| In order to avoid a metal to glass contact and insure distributed loading, corner strips 5858 of resilient material are inserted circumferentially about the corners of the respective sections l0 and ll of the pump casing, and the inner corners of the frame sections 50 and 5|. Rubber or any other highly resilient material may be used for this purpose. As will be observed from study of Figs. 1 and 7, frame sections 50 and'ii are so contoured as to bear on section l0 and II of the pump casing only adjacent their peripheries and particularly on those portions of the end wall sections in alignment with the outer circumferential wall of the section II. Raised bearing surfaces are provided for this purpose in the corner of frame section 50 which are preferably accurately machined. These raised surfaces in cooperation with resilient strips 58 provide clearance between housing A and chamber B at all points except adjacent the periphery of the latter.

Of course, the elements of the stufling box or gland between the impeller and the casing section ment of the pump casing within the metal frame but in order to facilitate such assemblage and to provide for adjustments of pressure against the gland, and to facilitate take-up occasioned by wear, temperature, or other conditions, the rear of the housing A, i. e., the section 50, is formed open, and adjustable means are provided for effecting a closure thereof. To this end an annular ring-like plate 59 is provided with a central opening 60 of a size large enough to surround the hub of the impeller and the drive shaft therefor with ample clearance. The purpose of this plate 59 is not only to close the opening of the section 50 but also to apply a yieldable pressure against the elements of the gland, and it will be observed that the sealing elements I! are backed up with a follower 6|, preferably of glass, or of material having the same expansion and contraction characteristics as the material from which the pump casing and impeller are made. This follower will be assembled within the gland and backed up by packing of resilient material, indicated at 62, which in turn is backed up by the plate 59. Studs 53, threaded into the section 50 extend freely through perforations circumferentially disposed in the plate 59, and carry at their outer ends take-up nuts 64. Interposed between the nuts 64 and the outer face of the plate 59 are springs 65. In the preferred embodiment of the invention, studs 63 are'threaded for only a short distance at either end and the length and strength of the springs 65 are so chosen that they will never be fully compressed when nuts 64 are drawn up to their extreme limit of travel. Thus the pressure exerted on the follower GI and packing by ring plate 59 can never exceed a redetermined maximum pressure established the characteristics of springs 65.

It might be noted that the elements [1, in addition to functioning as a seal in a stufling box or gland, may be formed of material effective to dispose of frictional heat and transfer same from the point of heat development. A suitable packing for this purpose may be prepared from asbestos fibres, lead shavings, and graphite.

From the foregoing it is evident that a controlled and predetermined pressure is exerted on the stuffing gland and transmitted through the stufling box assembly, through the compression afforded by the springs 55.

Referring nowto Figs. 6 and 7, it will be observed that the essential elements therein are substantially the same as illustrated in Figs. 1 to 5. However, the supportinghousing or frame A for the casing B, instead of being bolted or otherwise secured to the motor M, is provided with a standard 66 having a substantial base 61 and arranged to encircle the neck or hub-like portion 68 of the housingA. Provision is made portion of the standard made separable from the base and leg portions to facilitate assemblage. In this event bolts 12 entering the socket portions 13 may be utilized to secure the standard in position.

, standard may be made an integral structure.

, It has been stated heretofore that variations are possible in the joint and bonding media betweenll might readily be preassembledprior to place- 7 5 the driveshaft and 'hub of the pump impeller.

This,-however, is optional as obviously the I Fig. "1 illustrates one such variation in which the hub 18a of the impeller I is provided with circumferential inner grooves 23a of substantially uniform depth throughout, such depth being equivalent to that of the longitudinally extending grooves or flutes 82a. In this arrangement it is contemplated that connection may be made directly to a drive shaft (not shown), or to a quill, but the tank 21 (Fig. 2) may be omitted in the form shown in Fig. 7.

Figs. 8, 9 and 10 illustrate a somewhat further modification or embodiment of the invention, in which the volute l5 and the closure plate 18 are arranged somewhat the reverse of the showings in Figs. 1 and 7, and in which the mode of clamping the frame sections and easing members .15 and I6 1 is different. In this embodiment, we find the volute on the forward or outer portion of the pump casing, extending outwardly into an eye or inlet 11, and forming a pump chamber, when assembled for the impeller I. A discharge 18 extends radially outward instead of tangentially, but this arrangement of inlet and outlet can be varied to suit a particular installation. This arrangement of housing parts is particularly desirable since by merely removing the volute 15 access may be had to both the front and back of the impeller plate for cleaning and inspection without further dismantling the pump.

The housing or frame in this form of the invention is primarily for supporting purposes, and

for holding the glass pump casing in a properly assembled, shock absorbing relation, there being no outer frame or housing about the main exterior of the glass pump casing.

The volute I5 is formed with an outwardly, radially extending flange .19, and the section 16 has a similar flange 88 which merges into a shoulder 8|. When assembled the flanges 19 and 80 will be abutted, and the shoulder 8| will fit within the. periphery of the bell of the volute 15. While no gasket is illustrated between the flanges l9 and 80 (Fig. 10), it will be evident that any suitable packing or gasket may be utilized, as desired, and the base of the flange 80 is channeled, as indicated at 82, for the reception of packing at that point.

The frame or housing for supporting the pump casing takes the form of an annular member 83 secured to struts 84 which extendrearwardly to the motor M and form a support for the pump assemblage. Metal clamping pads 85 which may placement exteriorly' of the flange l9 and volute 15, as outer supporting or retaining means for the assembled sections 15 and 18. e

In order to secure the parts in assembled relation, ears 86 are formed on the annular section 83 of the frame, these ears, together with pintles 81, forming hinges for clamps 88. The clamps 88 are provided with pressure adjusting screws 89 threaded into lugs 90 and efiective, after assemblage of the parts as an adjusting means for holding the pump casing sections in proper relation under desired pressure. Gaskets 8| and 92 function in a manner similar to the gaskets 5858 of Fig. 1 to resiliently protect the glass casing sections and prevent a metal to glass contact. 'It will be observed that the "described structure is particularly adapted for quick and easy removal of the volute 15 since screws 89 need only be slightly loosened and clamps 88 swung back on their pintles 81 to completely release the volute I! from the section 16.

The struts 84, in addition to supporting the pump on the motor, which incidentally is itself provided with supports indicated generally at 93 provide a means for mounting the face plate or pressure applying medium to the stufling box. As shown in Fig. 9, the plate 58a is entirely supported by bolts 63a, circumferentially disposed in suitable openings adjacent the periphery of the plate 59a, being in turn mounted in lugs 84 which are formed on the respective struts 84, instead of being secured into the frame or housing proper. Pressure adjusting nuts 64a control the pressure applied to springs 65a in a manner similar to that illustrated in earlier figures of the drawings. The other features of the pump structure and of the joint are in all respects similar to those heretofore described in connection with other figures. i

What is claimed is:

1. In a glass pump structure, a pump chamber formed of a plurality of separable glass sections and including a generally cylindrical circumferential wall, a protective, supporting metal housing for said chamber substantially enclosing said chamber, means to assemble said housing about said pump chamber and by such assemblage, hold said chamber sections in assembled relation, highly resilient means associated with said chamber take the form of a complete annular ring, but "as illustrated are spaced pads, are arranged for and housing effective to insure distributed loading of the pressure of said housing on said chamber, said housing and chamber parts being provided with contact surfaces of restricted area extending about the periphery of the chamber and in substantial axial alignment with the circumferential wall thereof.

2. In an all glass pump structure, a glass housing comprising a section having a central opening, a glass sleeve integral with and extending outwardly from said housing concentric with said opening, a glass impeller member positioned within said housing and having an integral hollow glass hub extending laterally through said opening and said sleeve and substantially coextensive in length therewith, packing having a high thermal conductivity positioned between said sleeve and said hub and substantially filling the space therebetween, and a metal driving member filling the opening. of said hub whereby said hub is positioned between members of high thermal conductivity.

3. In a glass pump structure, a pump chamber formed of a plurality of separable glass sections having abutting ground glass surfaces in axial alignment with the circumferential wall of said chamber, a protective metal housing substantially enclosing said chamber and. adapted to support and hold together said glass sections, said housing being designed to bear on only those portions of the chamber adjacent its periphery which are substantially in axial alignment with the ground glass abutting surfaces and the circumferential wall of said chamber while being spaced from said chamber throughout the remainder of its surface, and highly resilient non-metallic means associated with said chamber and housing and located about the periphery thereof to insure distributed application of pressure by said housing on said chamber about'itsiperiphery to hold said glass sections tightly together.

4. In a glass pump structure, a sectional pump chamber comprising a disc shaped end section V and a hollow body section, said body section includmga generally cylindrical portion forming the peripheral wall of said pump chamber and an integral web forming the remaining wall of said chamber, a sectional metal housing substantially surrounding said chamber and supporting said chamber sections in abutting relation to one another, said housing being so shaped as to provide flat bearing areas for said chamber sections of limited extent atfitheir peripheries and immediately adjacent thereto, spaced coacting means peripherally disposed about said housing to draw the sections thereof toward one another thereby applying compressive force to the chamber sec tions substantially in the plane of the peripheral wall thereof, and highly resilient non-metallic spacing means interposed between said casing and said housing effective to insure distributed loading of said compressive force about theperiphery of said chamber.

6. In a glass pump structure, a pump chamber comprising a substantially flat glass face plate forming one side of the pump chamber and a hollow glass body including in one integral piece a substantially cylindrical peripheral wall and a substantially flat faceplate forming 5. In a glass pump structure, a sectional glass pump chamber comprising a discshaped end 'section and a hollow body section formed with a cylindrical peripheral wall and an integral disc shaped wall extending across one end thereof, a

discharge pipe extending tangentially from said cylindrical wall and formed integral therewith, circular'flat joint surfaces on said cylindrical wall and said end section adapted to be brought into abutting relation to one another, a sectional metal housing substantially enclosing said chamber and supporting said chamber sections in abutting relation to one another, fiat bearing surfaces on the transverse walls of said housing sections adjacent the periphery of said pump chamber and in alignment with the cylindrical the remaining 'walls of the pump chamber, and

a protecting metal frame enclosing a major portion of said pump housing, said frame having circular seating surfaces in axial alignment with the peripheral wall of said pump chamber, and means for clamping said frame about said housing whereby the chamber parts are held together by compressive forces applied directly in align ment with said chamber periphery so that primarily compressive stresses are developed therein, the'remainder ofsaid frame being spaced from said glass parts;

'7. In a glass pump structure, a pump chamber comprising a substantially flat glass face plate forming one side of the pump chamber and a hollow glass body including in one integral piece a substantially cylindrical peripheral wall and a substantially flat face plate forming the remaining walls of the pump c tecting metal frame enclosing a major portion of said pump housing, said frame having circular seating surfaces in axial alignment with the peripheral wall of said pump chamber, and means for clamping said frame about said housing whereby the chamber parts are held together wall thereof, spaced clampingmeans for holding by compressiveforces applied directly in alignment with said chamber periphery-so that primarily compressivestresses are developed therein, the remainderof said frame being; spaced from said glass parts, and resilient packing material positioned between said glass parts and the seating surfaces in said frame.

wnman A. m'rns.

her, and a pro- 

